Gear-and-pinion transmission.



2 SHEETS-SHEET l.

Patented Nov. 4, 1919.

A"GEM AND Plmon APPLICATIUN FILED IULY 3| ?-cul A fr 'x G. EDWARDS. GEAR AND P|N|0N TRANSMISSION. APPLICA'HON FiLiD IULY 3l. 1916.

@meenemen Hummm v Siieifdativxi ,Q1 Intim @met Patented Notti, 191,9.

To aZZ-womfz't man .concerner Be it known t at I, @notion Enwmmsta citizen of the` United Stinnes, residing ab Berkeley, in the county' et Alkemade.' and.. State of California, have-invented new endl useful Impnonementsl inwGleanewndPinion Transmissions, .of which the-folioming is a. specification.

These specification and: drawings 4ere in` tended to disclose the art of avoidingde structi've stresses of'torsion, Whew transmit; ting power between twoA shafts, by IneensV of intermeshed teeth; endl wiso mechanical ineens for applying this art. The main field lies in the use of more than two genes, or toothed means, connected with one ofthe shafts.

The torsion imported to ashnft by trenemit'ting'its normal full load: is usuaily estmnted; et about one degreey of :n cinele for each ten feet of shaft. It varies, however, as the load rises. above, orY Bills below,- its normal'. W'hen Such e.t shaiit .ceiviese pinion, which engages with e gear wheel", the torsion of the shaft is imparted tothe pinion toV an extent varying Wilili the ratio. oli diameters.

If the pinion is integral with: the shaft smi-ii of the seme diameter On the pitch iinieyt'lhe torsion of the pinion will be substantially' the same as its shaft.

If We assume that the teeth ofthe gearv wheel, that is driven by the pinion, :arenot twisted out of their normal direction., por nllel with the shaft of the gear Wheel, and are rigid; and that the pinion teeth allso vare rigid, exceptus twistedlfbytorsionithen there will be but one point'ofiaintelctlIhre?` tween the pinion tooth and? th coriespfmd ing tooth of the gear and? this point mill' be. nearest the source of power, as will [be admmed northern etremrnlentnly bytlieiborsio; 'f- L This; beweren-2in ctnel practilegis not the easejfontlae meson timtfthelppiniorerdf i A This iiegemi.' and pinionwililseve about187 in-lel .over the hest 'of .other devices, .pmo-

the geen#teeth .eine not Tig'idivbitrelastio. Pressure, {tlierelformbetween the pinion 31ml the ear/teeth, may-tithe pince-Jip to the. elastic limit If theeomtactpressnros item4 riec'l beyond-the elastic liminone or beth teeth# limiet be-bentotbrolen'.; r

The pressure of the pinion? tooth upon; the corresponding tace of the gewitooli fvries with fthe extent to which theteebh are i tic/sillyA bent heelnwwrd, aindldeerleases, cwi

to torsion, with thenlfistamee the slm a from `the source oil peWeif: 'Andes thereiis wa'ndl, it ffolllnws that.: there is etA limit] alsoE to length of fece O the teeth, beyond Whmhfneadwantage is gainedl In pnactice,

this.i li'miir spinners to be about eighteen,

innms; Thupmssure oi the pin-ion tooth upon bhecgeer toothi diminishes with the distance frrmni the point of Contact nearest the sourceoiE-pomer'm'a point about ei hteen inches theoemm, and it is not consldencd goodl rpgwtietopusln it familier; for little 1s to gal-med in extending the width of fafcetoy the vanishing point of power treinsmission.

@Wing to this; torsion.` and toV the nesillient limit oi" the teeth in contact, there has been n limit, heretofore, .to the amount of power that een be transmitted safely by e single pinnenn andi geen mowing to luck Bof.' ac commodation` for torsion, it Vhas not been possible, henetoore, to usei ai suceeesion.y of pinions; .ci the maximum possible length@ with the exception -o' the special case of right and ledit helicail teeth, which enable tbe'praotical limit yto be doubled, "because y speed-.of rotation `give an eniency oiflibutout 90%.

vided thwt alill the other elements that .enter into fuel consumption are exactly equal;

Fui-warmere, thelelioiency of a. steam eine bizne rapidly amenant 'of its home-power: 'The development oflmerfim practico, dneredomf' Shbuld "be `the direc` tion of concentrating all the power in e ,grotV its'most efficient d, anelitrdfnt'mgits power teeny desired number .otf screw lm'ciglV more: than abonn. f eighteen inches isi not required. The ybest of 'otiherdevices fmetmmsforinin It is the object of my invention to retain the above large eiliciencies1 of pinions and turbines by enabling the 'gear' and p'i ion to transmit powerI of any amount., Instead of limiting the power delivered by one pinion shaft to about, 3000 horse-power, as is usual in present practice,` I purpose to use a single pinion shaft to transmit up 50000 horse-power, and beyond that amount, if required.

The amount of circumferential displacement of the gear and pinion teeth, by torsion, which should be adjusted for by the flexibility of the teeth. or by some other means, will vary directly with the diameter of the shaft; if the pinion has'the' same torsion as its shaft. If the diameter of the pinion shaft is doubled to transmit four times the power, the circumferential dis placement will be doubled in amount, and if the amount of torsional displacement that is compensated for by the elasticity of the teeth is held as a constant. the Width across the face of the gear and pinion must be re# duced one-half. This condition that the width of the working face must be reduced as the power transmitted increases, is one of the sources of difliculty in the application of the gear and pinion for transmitting high powers under former designs.

The adjustment required for torsionV will become clear if We take the exampleV of a pinion shaft 5 inches in diameter and assume that the pinion has substantially the same diameter and the same torsion as its shaft. If the pinion is 18 inches wide-there Will be .0065 inch torsion across the face of the pinion under normal -full load. f If we introduce an intermediateshaft for a bearing 15 inches long and divide the pinion into two segments, each 18 inches long. on each side of the bearing, giving a total length of 51 inches, the torsion will be .0184 inch. If the same dimensions are maintained and 3 intermediate bearings are used, and 4 pinion segments, giving a total length of 07 inches over all, the total Atorsion in this length will be .042l inch.

Furthermore` if We `assume'in the above earssh-aft iscarrying..

illustrations that the its normal load and t at the gearsegm'ents are each carried on anseparatefdruim there:

will be a displacement in the gear ifa-ces.

due to torsion in theshafnin the-ratio Ooil? diameters of the pinion andglear. If this ratio is 10 to 1 the torsion of thel gear face will be .42 inch. i s

Obviously, such variations astheseare more than suiiicien't to'. cause destructive' stresses in the teeth-cfa gestrand pinion when transmitting high.v power,` unless c'ompensated for.

My invention givesperfect are(iomnieda-V a.i l z gear and pinion. It enables the correct contactd pressure on gear and pinion teeth to b'e standardized, so thatY in designing gears pinions the correct Width will be the total power transmitted at the required face speed multiplied by the standardized pressure per inc of face.

`I gain an additional advantage by interposing elastic means through which power is transmitted between the pinion and the gear shaft, which will absorb shock and vibration, that are especially marked in the marine screw shafta-nd in rolling mills. It also tends to smooth and quiet running.

In the accompanying drawings, Figure 1 is a diagrammatic view illustrating the torsion of a shaft and pinions, under full loads, the pinions oii'ering the same resist- :nice as the shaft; Fig. 2 is a broken plan view., the casing being removed, of driving and driven shafts and pinions and gears thereon` with a detachably connected steam turbine; Fig. 3 is a transverse sectional view; Fig. 4 shows part of the power transmitting mechanism in a different position from Fig. 3; Fig. 5 is a section on the linz` 5-5 of Fig. 3, the pinion being on'iil'ted: Fig. 0 is a section on the line 6 6 of Fi 3; Fig. 7 shows a different form of drum troni Fig. 2 partly in cross-section and partly in .plan vieW; Fig'. S shows a cross-section 'of Fig. 7 on the line Ss-S, and part of the powertransmitting mechanism; Fig. 9 is a broken plan view of two drums of the type shown in Fig. 7 Fig. 10 is a cross section of an alternative method of connecting part of the power-.transinitting mechanism; F ig. 11, partly in plan and partly in cross section, shows seats for the springs when at rest; Fig. 12 shows an alternative means for holding part of the mechanism in working position,

Referring to the draiiings, l indicate a pinion shaft. rotatable in bearings and 2. and 3 a gear shaft rotatable in bearings 4 and a. The gear bearings are supported by arms 50. InFig. 2 the upper bearings are removed and the lower bearings only are shown.

Integrally with said shaft and located between bearings are formed right and left helical pinions 6, which engage right and left helical gearrings 7 and 7 one ring being operatively displaceable circumferentially relatively to another ring, and also relatively to the` surface of the drums 8 which are keyed tothe gear shaft, as shown at 9. I mean such power-transmitting means as these gear `rings and the supporting drums and the variations of constructionwhich I shall indicate, or their equivalents', by the phrase, inthe claim-s "a portion of the power-transmitting means of said second shaft being operatively displaceablef'circumferentially relatively to the renaam mainder, referring to one segment' of a power-'tranmnitting peripheral face relatively to another segment and both segments being operatively connected with the first e shaft for transmission ol power betweensaid two shafts. Byv the phraseopemtively displaceable circumferentially relatively to the remainder, as inl my claims, I do not ineen the slight distortion of teeth and metal across the face of a gear ring, or its equivalent, or in any of the solid transmitting parte, under the stress of the load a ndtorsion.

It is obvious that the two shafts 1 and 3 may be more Widely separated and the powerstransmitting peripheral faces of the pinions and of the gear rings be modified, so that power may be transmitted from one shaft to the other by any kind of belting, or equivalent means. Intermeshing teeth, with the operative means by which said power transmitting" faces are operatively connected with their respective shafts, is what I mean by the phrase power-transmitting rotary means operatively connected with the first shaft, power-transmitting moans operatively connected with the second shaft. as used in my claims.

One gear ring 7 is movedl in an axial direction tol position on said drum and abuts upon an ontwardl extending liange 11 of saidi drum, theotier gear ring having in- Wardly extending arcuate rilsflQ, which can slide axially into recesses 13` on the drum, and then may be turned circumferentially to enter circumferential grooves 14 in the drum, which retain the ring in its operative position. The number of such ribs is limited only by the requisite supports and the operative play of the gear rings on the drums. It is obvious thatthe faces ot the drums may be Wider and one or more additional gear rings be placed between the two rings indicated on asingle drum, (Fig. 2).

Rotatably mounted on the extremities of the hub of the drum are circular yoke's 16, from which extend, preferably'two laftes 17 to whichl are' bolted afr'ms 183, Whi 'extend through circumferential; slots 19 in the' drum anddiavefon their 'outerends lingers 21, which-entier* corresponding recesses 41j inthe inner side of the' gear-*ril`igs}` Careful Afittingr to a hearing may be avoided 'by melting the recess 41 le'rger than the lingers 21, and by filling thespaee with Babbitt or the like metal lf, as shown' in my Fig. '10'. Thearm 1S- carries a 'hall 20 `supported by a, threaded extension- 22'that is inserted! inthe arms 18. The ball entersfa soeket in a carrier 39 for one end of a: spring 24.; 'Ilheopposte end' of the spring-is carried byr, corresponding socketed support and ball 25, attached to the drum 84 totramsmiit power to rar-,from the' lilium and thence to or fromltlae shaft 3i. The balls-l afre adjustablie, so that each: spring,

having beenA testedf separatelyr and' its exact- ]ength measured at -fl11lloa|d, magyy lbeset to carry its exact share' of the fulll yworking' load by compensating for the distortion cruised: by torsion, at thepoint where ewoh .sp-ring is located, and' also to adjust for any lack of unifbrmity between the springs. When the ball-s are lroperly adustedi to position, theyma hek eld in place by abinding nut 27, on y a clamp 28, or like device. If the motion of the liniori and'4 gear is intended to be reversib' e, a like construction of balls sockets, springs and connections therewith, may be used to transmit the load. When the sprlngs are at rest they ane supported (Figs. 2 and 11) in a' recessed support 38 for the spring carrier 39, the sup- Brr port being attached to the drum. The sup- A port 38 may be movably attached to the drums and so permit adjustment for varia* tions in the springs from the desired tension.

In the application of the springs, two methods are available: (a) all the springs may have the same length Without loa-d and have the same flexibility; (b) all the springs may have the sanne length Without load` but gradually increase in stiffness according to location in the same ratio with the increase of displacement by torsion, which may be done easily by gradually diminishing the diameter of the coil from one spring to another. TheseA two methods permit of seientifio precision, but, of course, the method of applying the springs may be varied indefinitely.

To illustrate the methods (a) and (b), let it be assumed that the gears in Fig.. 2 have a lafrge diameter and that the maximum torsion is 2 inches; and that thel gear rings are displaced 6 inches from their at`rest position bythe pinions in Ibringing the springs to full load. Let us assume. for clearness of illustration, that the pinion shaft is with out torsion. Let the power he delivered to the pinion shaft onits right end and the gear deliver its power at the left end; In case (a) let the ball` 20 be in full Contact 'with its 'spring socket on the right-hand gear, and in the left-hamd gear let the ball be se erased 2 inches from:l its sprin vsoelmt 2%. When the pinions have displaned the'grear rings 2 inches, the ballon the lleft Wi'llfhave reached its socket, but the spring' will. be Without loadi @n the right, however, the ball will have compressed. iltsspring 2^ inches,

or to onedhird load and onemhiird of the ment-,is made upf on bhalefthy free ,peyrof theibnllfandron theright b torsion. 1 yhe saine ,.princ' le holds with` .t e intermediate.

the'pinions havevdisplaced theg'eerv rings yG.,

inchesfrom thetatrest positions ,up to full louldwhe spring on the'left willfbecompressed* 6. lriches, Whilethe spring on the 1ig ht,beingv stitfeh, will be compressed but 4 1nches,.and the remaining 2 inches will be made upof .the torsional displacement.'

Itis obvious that the equalizing element is of: such,` construction that the designer may incorpdrateamarglin of safety, soi that, on failure ofso'meof-the earrings, up to the limitI of such margin, t e load will be carried safely by theremaining ear rings.

To; `autolfnntioally adjust or accidental errors in longitudinal alimentent, I cut ont a minimlun=space of the'teeth 29 at the verticesfofthe right and left helices of .the pinion; orlof theteeth 30' of the gear rings, so that the gear segments may automatically adj ustV themselves properly.

In F ign? the end of a steam turbine casing is :indicatedwby f31` and :oneend of its shaft is detachably connected tothe pinion shaft l byntiheyooiipling .32andi 33 connected by "y 1 i Figs. l and `8 show2 a different ferm of drum', inK which the shell of the 1drumft trans` initsthe load.r to its .operatiieishwt 3. The.

pur ose of this construction is to reduce tors onftof a 'minimizing or to; cheapencon struction. 1If the load r' uiresy the` use of two such drums (Fig. i9; they may be laced on each Side of an intermediate bearing 4" and both beke'yed to the shaft 3 in ju N4aposition tor-thisbe'afrin-g. :The end* 36 of-t second drum issupported 'by-the shaft 3 but is lnot keyedtheretoln Fig. 7 the crossfhar of :one ringris et right angles to thatrotfthek next The wond keyed isifintended Sto? coverzany. rigid connection. Thetform 'thedrumlsllwniirFig. 7 may also 'be used tueallny but: a singile group f power-tivalriittngs? ringsg the l nemer; f such ringebeingr indemfte Lf thef number of'r' te itefspokes: to finte'mfre with the crossbarrs andfsprings. ffl

The. operative'.circumferential displace mentrelatisely to iieeup-portin element of thel poweretnialsmittngniearis oshzaft 3 will varyl eecniiing' l the 1 constucion. 0bviouslyf thegear key 9! `nitty :be vvrenicnved and thefbiilll Befooimeoted.- with enorm that; .iswleyedtoithei shaft. lnthis ease dis-r plamentf'might take eiouitlid shaft, or; onrftihmndiun'ior on= oth, 501', the; lehe-ftd might he surrounded. hyza bushingyfor by.

a sef'ies of'superim osedbushings, s tlpliiortd ingr-theI drum, or t, e irummight 4lgm'fs'ul fis @dd-,z ltli Aconstructitin :has fno .inL`

ported by .afiriction clutch 42,'-Fig. 7,-e,nd

thedsplacementbe divided among. all these supporting elements. t

For clear-ness, I show most of the available interior space of the gear (Fi s fB end 4) occupiedfby four springs and` t eir connections, hilft,Y npreetice, .this willihe the case only with small eersy By the phrase Tresi iently connected with thelsecond shaft, as, used.- in the claims, I mean-the 'interposition of a resilient or elastic element through which the power is transmitted, and that this resiliency or elasticity is greater than, or in addition' to, the slight resiliency or elasticity that is normally'present in the teeth and in all the metallicparts `of an ordinary gear ,keyed to o its shaft, or itsequivalent, in a solidly con.-

tivelyito the remaining ,faces,jand, to the supporting. element. l v

when the means i for, l ,compensati `for tension, v,is nelastie,.the eirloulnferentii Tdisplacement of oneV ppwentransmitting face relatively to another face and relatively to the supporting element is mainly a correction forv torsion. When an elastic element is used, as shown in my drawings, there is added adiisplacement relatiyely to thesu porting element due to the; elasticity of t e means through which the power is trains mitted My claims .are ilrlldedpto cover the first case; and, also the SCOnd case combined .with the-rst,.i used.

i009. .pounds perincliisgeonsidered es.

about the :Safe 'marimumfory i teeth opera:

tionA feiueontact pressure between.-rgeer,andv vpmaonn when freed frein-the weakening ef,-

feot efftorsion.' It-,ffollowa thereforethat this presentes multiplied inte the `Width of the face, ci? 'e gear ring, will fgive the maxi` mumlead placed uponnthe springs, This.

`10nd.runter rises aahoy/e a moderate burden fontwofsprings, althou h more springs may bernested .together andgnsed iiprezferred;

vBjr-'keeping the 'pinion at about the! same districten onfits pitcliflineas its shaft,L the dameterfot thengeerf-is `kent at a miniP fvg lffi Myipneferred constituation.listo use, .for

gena'fand'pinien, right, and left helical i teeth; slanted se ses .to press the operatively other instealdof stiggerefdand the inipns the ace of their Lazcano ldisplaceable gear rings together when 0n the forward rotation. On the reverse rotation, usually at not .over half power, the rings .will be pressed against their side supports.

My construction is such that the torsion of the gear sliai't, or of thegear drum does not distort the gear teeth,` although, ot' course, they are operatively displaced circuinlercntially 'relatively to the supporting element and to each member of the series of gear rings by such torsion and by the elasticity of the sprin fs. And it is obvious that my correction or torsion is by the segmented, or step by step process. Between tlie steps, 1 rely on the elasticity of the teeth for adjustment.

Power may be imparted from the drums through a friction eluteh,.if it is desired for any special purpose. A conventionalized clutch is shown at 42 in Fig. 7.

It preferred, the power rin s may be held in position as shown in 4ig. 12, the drum being grooved, and an open band 45 of cold rolled steel inserted in each recess liti and held in position by as niaiiy countersunk bolts '-17 as may be necessary.

It a pinion engages more than two gear rings, a slightly better contact will be ob tained between the ear and pinion teeth, ifa minimum space is, cut oifityof thelpinion, as at 29, to register with each division line between the gearring'lsgf roots ci the pinion teet ifshiou e cut below shaft, so that the' Flexibility of the teeth may not be reduced.

I give the following examples to illustrate the applications of iny invention, the pitch lilies of the pinions being of the saine diameters as their shafts:

It 10000 horse-power at 2000 revolutions per minute is transmitted from a single pinion shaft to a single gear shaft, with speed reduction 15 to 1, with 3 feet circumfei'ence ot pinion, with 80 inches of gear face, with lcontact teeth pressure of 688 lpounds perinc'hg, with' ear rings'having 10 inches across. faceen ABrings in all, carried in pairs on 41, separate drums, with 3 intermediate bearinigs'qr pinion shaft i;

and gear shaft, Wi a total over all length of gear faeesand' ,intermediate bean. ear ries trees.

ing 0110A: feet,andeaehwgb Y initting powerl through EZ sprin' s, each gear rin will transmit 6880 penn s load; each spring Willcarry about 3600 ,p load; the torsion of the pinions and their shaft will be .1l inch; thetoiision ofthe gear teeth will beuover 1.25 inch. Or, fflv the lpewter is distributed vtroni onepignionjshjaft e of drum to twogear shafts, using tli'etyt shown in my Fig. 7, the drumseach :icing haring one'finterni late' bearing',y t e'torsion of the pinion shat atfitlllflead will. be p ",perlminute is transmitted from a single inien shaft to twg gear Shafts, dp

Vof pinion, with 252 inches of rrings 6 inches wide and 71g 4 torsion of the, pinion E andofthegear faces 2.3 inches.

.05 inch, and the torsion of the drums will vary accordi? to the stiffness given to their shells. he load on the sprin s may be carried by springs made of ine steel, withabout inches outside diameter of coil, 14 coils, free length of 20 inches and about (i inches compression at full load.

1f 2.0000 horse-power at 150() revolutions er minute is transu'iitted from a single pinion shaft to one gear shaft, with speed reduction of 12 to 1, with 4 feet circumfer- ,ence 0f pinion, with 192 inches of gear face, divided into 24 gear rings, each ring h auing 8 inches across face, with 4 gear rings .on each drum and 6 drums, with each gear ringtransmitting through two springs, with. contacttooth pressure at 572` pounds lper inch, with 5 intermediate bearings for ,gear shaft and pinion shaft, with 22 feet' over all length of gears and intermediate bearings, eac i gear ring will transmit 4576 pounds load; each spring will carry about 2500 pounds load; the torsion of the pinion shaft will be .29 inch; the torsion of the gear faces will be about. 3 inches. Or if the power is imparted from one pinion shaft to two Agear shafts, using the type of drum shown 1n my Fig. 7 the pinion having two intermediate bearings of E24 inches each, the torsion in the Jiuion will be .16 inch, and the torsion in the gears will vary With the stiffness given to the shells of the drums. The over all lengths of the drums-will be 12 feet. Y A j .T here is no important gain by using the forni o` drum shown iii Fig'. 7 in reference to the drums shown in Fig. 2, as 'the springs can be adjusted easily to compensate for inaxilnuni torsion. The type of drum shown in Fig. 7 is better adapted to carry two sets of gear rings, with one intermediate bearing for the pinions, as giving a more satisfactory length of drum, than for a greater number of sets and bearings. Ordinarily, the construction cost will be the determining feature in a choice between the two types 0f drums.

If 3,0000 horse-power at 1000 lrevolutions with spee re- 10 to 1, with 5 feet circumference gear face, with.` contact tooth pressure 4of 786 pounds per Anch, carried by 3 separate gear drums, t with two intermediate bearings for the pinion shaft and each gear shaft, with 14 feet length over all of gears and intermediate` bearings,V with geur ear rings duction Y Q y y to each drum, With each gear ring transmitting power through 2 sprin fr,yeaclifgear ringY will transmit 4800 pouni load; each spring will carry $260.0 {501111115} lOafd; the, mxlrn'um shaftwill be .2 3 inch o ratively and resiliently pinion and gears;

two shafts, comprising The following illustration is given to show the gain in eiliciency by the use of'my invention: y

In the case of a ship using 8000 horsepower on each of 4 screw shafts, let it be assumed that, if the screws are driven by 4 direct connected steam turbines, the Steam consumption will be 13 pounds of steam per horse-power` hour and that 'the screw loses in eliciency by hivh speed of rotation. In comparison, let it he supposed that, by using my invention, a single turbine supplies the 32000 horse-power, with a steam efficiency of 8 pounds of steam per horsepower hour, that the screw revolves at its most efiicient speed, thatrone pinion shaft transmits power to 2 intermediate shafts and that each of their intermediate shafts transmits 8000 horse-power to each of the outside screw shafts by means of my torsion compensating gears, that each toothed power transmission will entail a loss of 2%, then there will be a net gain of 4% in the 7% gain in the screw and the 3% loss in the the steam gain will be .38% in efficiency; or a total of .42%. This will be the saving in full, in the space required for fuel and boilers, which may be used to earn freight money, and the eonstruction cost in the engine room will be reducedat least one-hal 1. Means for transmitting power between power-transmitting rotary means, carrying teeth, operatively connected with the first shaft, more than one power-transmitting means, carrying teeth, connected with t ie second shaft, the first teeth intermeshing with the second teeth to transmit said power, at least one of the second powertransmittin means being operatiyely'displaceable re atively to another and adjusting mechanism for varying the operative rcsistance of said resilient element, to avoid destructive stresses fof torsion.

2. Means for transmitting power between two shafts comprising power-transmitting rotary means, carrying teeth, operatively connected with the` first Shaft, more -than two power-transmitting means, carrying teeth, operatively and resiliently connected with the second shaft, the resilient element not being integral with the means that carry said second teeth, the first teeth ing with the second teeth to transmit said power and atleast one of the second owertransmittin means lbeing operative y `displaceable re ativel'y to another, t'o avoid destructive stressesof torsion,4 the resilience of the equalizing element beingthemeans for attain), g thesub-stantial equalization.

3L ,sans for transmitting p'o'wer between two shafts. compri ing power-transmitting rotary means, carrying teeth, op-

interniesli-4 ment, to avoid estructive stresses of toi'- sion.

4. Means for transmitting power between two shafts, comprising power-transmitting rotary means, carrying teeth, operatively connected with the first shaft, more than one power-transmitting ring, carrying teeth, o eratively connected with the second shaft, tie First teeth internieshing with the i second teeth to transmit said power, a drinn supporting said rings, the interior face of said drum not being in immediate contact with said second shaft, at least one of said rinUs being operatively displacenble relativeqly to said drum. to avoid destructive stresses of torsion.

5. Means for transmittiing,` power between two shafts, comprising power-tranemitting rotary means, carrying teeth, operatively connected with the first shaft, more than one power-transmitting ring carrying teeth, olperatively connected with the second shaft, tie first teeth, intermeshing with the lsecond teethto transmit said power, a drum supporting said rings, the interior face of said drum not being in immediate contact with said second shaft, said drum being keyed to its operativeshaft only at one of its hubs, at least one of said rings being operatively displaceable relatively to said drinn, to avoid destructive stresses of toi`- sion.

6. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, comprising poWerti'ansinittii'ig rotary means carrying teeth, operatively Yconnected with the first shaft, more than `two AVpowertransmitting rings, carrying teeth,l ol eratively connected with the second sha t, thelirst teeth intermeshing with the second teeth to transmit said power, a ,drumfsupporting said rings, the interior face of said drum not being in immediate contact withsaid second shaft, and means lfor substantially equalizing upon the teeth of said rings the stress caused by transmitting said power.

v7. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, comprising power-transmitting `rotary means, connected with thel first shaft, more than two power-transmitting means, carrying teeth, operatively and resiliently connectedY with the second shaft, the first teeth intermeshing with the second teeth to transcarrying` teeth, operatively i r mit said power, and means for substantially equalizing upon the teeth of said second means the stress caused by transmitting said power, the resilience of the equalizing element being the means for attaining the substantial equalization.

8. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, comprising power-transmitting rotary means, carrying teeth, operatively connected with the first shaft, more than two powertransmitting means, carrying teeth, operatively and resiliently connected with the second shaft, the first teeth intermeshing with the second teeth to transmit said power, means for attaching a steam turbine to one of said shafts to supply said power, and means for substantially equalizmg upon the teeth of said second means the stress caused by transmitting said power, the resilience of the equalizing element being the means for attaining the substantial equalization.

9. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, con'iprising powertransmitting rotary means, carrying teeth, operatively connected with the first shaft, more than one power-transmitting means, carrying teeth operatively connected with the second shaft,

the first teeth intermeshing with the second teeth to transmit said power, and adjustable mechanism for regulating and varying the amount of power transmitted through at least one of said more than-one power-transmitting means.

10. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, comprising power-transmitting rotary u'ieans, carrying teeth, operatively connected with the first shaft, more than two power-transmitting rings, carrying teeth, operatively connected with the second shaft, the first teeth intel-meshing with the second teeth to transmit said power, a plurality of drums supporting said rings and at least two rings being supported by one of said drums, the interior face of each drum not being in immediate Contact with its shaft, and nica-ns for substantially equalizing upon the teeth of said rings the stress caused by transmitting said power.

11. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, comprising power-transmitting rotary means, carrying teeth, operatively Copies of this patent may be obtained for ve centi connected with the first shaft, more than two powertransmitting rings, carrying teeth, operatively connected with the second shaft, the rst teeth intermeshing with the second teeth to transmit said ower, a pluralitof drums supporting said) rings, and 4at east two rings being supported by one of said drums, the interior face of each drum not being in immediate contact with its shaft, at least one of said rings being operatively displacea'ble relatively to its drum.

12. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, comprising power-transmitting rotary means, carrying teeth, operatively connected with the first shaft, more than two power-transmitting means, carrying teeth operatively conneited with the second shaft` the first teeth intermeshing with the second teeth to transmit said power, means for substantially equalizing upon the teeth of said second means the stress of said transmission, and in the event of failure of part of said second means within a designed limit, the remainder of said second means being capable of receiving and of' operatively transmitting all of said power.

13. Means for avoiding destructive stresses of torsion when transmitting power between two shafts, comprising power-transmitting rotary means, carrying teeth, operatively connected with the first shaft, more than two power-transmitting means, carrying teeth, operatively and resiliently connected with the second shaft, the first teeth intermeshing with the second teeth to transmit said power, and means for substantially equalizing upon the teeth of said second means the stress caused by transmitting said power', the adjusted resilience of the equalizing element being the means for attaining the substantial equalization.

1liln the transmission of power between two shafts, consisting of power-transmitting rotary means, carrying teeth, operatively connected with the first shaft, more than two power-transmitting means', carrying teeth, operatively connected with the second shaft, the first teeth intermeshing with the second teeth to transmit said power, the art of avoiding destructive stresses of torsion, by substantially equalizing upon the teeth of said second means the stress caused by transmitting said power.

GEORGE EDWARDS.

each, by'addressini the "Commissioner of Patents Washington, D. C." 

